WO2010109653A1 - ターボチャージャの軸受装置 - Google Patents

ターボチャージャの軸受装置 Download PDF

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Publication number
WO2010109653A1
WO2010109653A1 PCT/JP2009/056305 JP2009056305W WO2010109653A1 WO 2010109653 A1 WO2010109653 A1 WO 2010109653A1 JP 2009056305 W JP2009056305 W JP 2009056305W WO 2010109653 A1 WO2010109653 A1 WO 2010109653A1
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WO
WIPO (PCT)
Prior art keywords
turbine
impeller
ball bearing
inner ring
bearing
Prior art date
Application number
PCT/JP2009/056305
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
正和 田畑
Original Assignee
トヨタ自動車株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
Priority to US13/259,242 priority Critical patent/US8602655B2/en
Priority to EP09842267.8A priority patent/EP2420660B1/en
Priority to JP2011505773A priority patent/JP5120494B2/ja
Priority to PCT/JP2009/056305 priority patent/WO2010109653A1/ja
Priority to CN200980158373.9A priority patent/CN102365440B/zh
Publication of WO2010109653A1 publication Critical patent/WO2010109653A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/027—Arrangements for balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
    • F01D5/048—Form or construction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/50—Bearings
    • F05D2240/52—Axial thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/50—Bearings
    • F05D2240/54—Radial bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/073—Fixing them on the shaft or housing with interposition of an element between shaft and inner race ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/08—Rigid support of bearing units; Housings, e.g. caps, covers for spindles
    • F16C35/12—Rigid support of bearing units; Housings, e.g. caps, covers for spindles with ball or roller bearings

Definitions

  • the present invention relates to a turbocharger bearing device that rotatably supports a rotating shaft of a turbocharger with a ball bearing.
  • a turbocharger bearing device in which a pair of outer rings are provided at both ends of a common inner ring to form two ball bearings, and a spring that applies a preload only to one outer ring is mounted (patent) Reference 1).
  • Patent Documents 2 to 4 exist as prior art documents related to the present invention.
  • an object of the present invention is to provide a bearing device for a turbocharger that can prevent the rotating shaft from being bent on the turbine side when assembled to the turbocharger.
  • a turbine wheel is provided at one end, an impeller is provided at the other end, and a rotating shaft having a large-diameter turbine side step portion formed on the turbine wheel side is provided on the turbine side.
  • a turbocharger bearing device rotatably supported between a stepped portion and the impeller, wherein the ball is positioned on the turbine wheel side and the ball is positioned on the impeller side.
  • the impeller side ball bearing and the inner ring of the turbine side ball bearing are restricted from moving to the turbine wheel side, and the turbine wheel side end of the inner ring is separated from the turbine side step part.
  • a positioning part for positioning the side ball bearing is provided.
  • the turbine-side ball bearing is positioned by the positioning portion so that the end of the inner ring on the turbine wheel side is separated from the turbine-side stepped portion. It is possible to avoid the inner ring and the turbine side stepped portion from abutting against each other. Thereby, it is possible to prevent the rotating shaft from being bent on the turbine side regardless of the machining accuracy of the inner ring and the turbine side stepped portion. Therefore, it becomes unnecessary to correct the unbalance of the rotating shaft accompanying the bending on the turbine side.
  • the inner ring of the turbine side ball bearing extends to a position biased toward the impeller side, and the impeller side end portion of the inner ring is restricted by the positioning portion. May be.
  • the unbalance of the rotating shaft is corrected by cutting a predetermined position of a rotating element such as an impeller or a rotating shaft, and the assembly of the bearing device to the turbocharger has corrected such unbalance. Complete later.
  • the turbine-side ball bearing is positioned at an offset position on the impeller side, the bending of the rotating shaft that may occur at the time of assembly to the turbocharger is concentrated on the impeller side.
  • the inner ring of the impeller side ball bearing is mounted on the outer periphery of the inner ring of the turbine side ball bearing in a state in which movement to the turbine wheel side is restricted, and the positioning portion is arranged on the impeller side.
  • the turbine-side ball bearing can be positioned closer to the impeller than the center of the impeller-side ball bearing. Therefore, the bending of the rotating shaft accompanying the positioning of the turbine-side ball bearing can be further concentrated on the impeller side.
  • the impeller side ball bearing may be integrally positioned together with the turbine side ball bearing using the positioning portion.
  • the impeller side ball bearing can be positioned using the positioning portion for positioning the turbine side ball bearing. For this reason, compared with the case where positioning of each ball bearing is performed by an individual positioning portion, the number of parts and the number of processing steps can be reduced, and the size expansion in the direction of the axis can be prevented, so that space efficiency can be improved.
  • a spacer interposed between the inner rings of the impeller side ball bearing and the turbine side ball bearing and having a width in the axial direction of the rotary shaft.
  • dimensional errors in the axial direction of the inner rings of the impeller side ball bearing and the turbine side ball bearing can be absorbed by correcting the axial width of the spacer interposed between the inner rings.
  • the processing accuracy of each inner ring whose level is increased by sharing the positioning portion can be reduced by using the spacer. This facilitates processing of each inner ring.
  • the configuration of the positioning portion can be realized in various forms.
  • a regulating member such as a pin may be provided on the rotating shaft as a positioning portion, and the movement of the inner ring may be regulated by the regulating member.
  • the movement of the inner ring can be restricted by forming the outer peripheral surface of the rotating shaft on which the inner ring is mounted in a tapered shape so that the outer diameter gradually increases toward the turbine wheel.
  • the inner ring of the turbine side ball bearing is provided with a protruding portion protruding toward the center side of the rotating shaft, and the positioning portion is directed toward the turbine wheel side.
  • a positioning step portion may be provided which is formed on the rotating shaft so as to have a large diameter and which can abut against the protruding portion. In this case, no additional member is required to realize the positioning portion, and processing is easy.
  • summary of the balance correction process performed in the assembly process of the turbocharger of FIG. The enlarged view which expanded the bearing apparatus shown in FIG. 1 and its periphery.
  • FIG. 1 shows a main part of a turbocharger in which a bearing device according to a first embodiment of the present invention is incorporated.
  • the turbocharger 1 is used by being attached to an internal combustion engine mounted on a vehicle such as an automobile.
  • the turbocharger 1 includes a turbine 2 to which exhaust gas from the internal combustion engine is guided, and a compressor 3 that is driven by the turbine 2 and compresses intake air of the internal combustion engine.
  • the turbine 2 has a turbine wheel 5 accommodated in a turbine housing 4, and the turbine wheel 5 is provided with a plurality of turbine blades 6 arranged in the circumferential direction.
  • the turbine wheel 5 is joined by joining means such as welding to the right end portion 7a of the rotating shaft 7 supported rotatably around the axis Ax.
  • a male screw 8 is formed at the left end 7 b of the rotating shaft 7.
  • a bearing device 9 that supports the rotating shaft 7 is mounted on a bearing housing 10.
  • the compressor 3 has an impeller 12 accommodated in a compressor housing 11, and the impeller 12 is provided with a plurality of compressor blades 13 arranged in the circumferential direction.
  • the impeller 12 is inserted in a state in which a rotation stopper (not shown) is provided on the rotary shaft 7.
  • An impeller nut 14 that meshes with the male screw 8 is screwed into the left end portion 7 b of the rotating shaft 7 protruding from the impeller 12. Accordingly, the impeller 12 is fastened together with the bearing device 9 by the impeller nut 14 and fixed to the rotating shaft 7.
  • a retainer 15 and a collar 16 are interposed between the compressor housing 11 and the bearing housing 10.
  • FIG. 2 is an explanatory diagram for explaining an outline of balance correction processing performed in the assembly process of the turbocharger 1 of FIG.
  • the turbocharger 1 improves the dynamic balance by performing balance correction processing in order to suppress generation of vibration and noise during high rotation.
  • the balance correction process is performed in a plurality of times during the assembly process of the turbocharger 1.
  • FIG. 2A first, balance correction processing is performed on the impeller 12 before assembly. While the impeller 12 is installed on a predetermined balancing machine BM and the dynamic balance is measured, the machining positions P1 and P2 set on the front end side corner and the back side of the impeller 12 are scraped little by little, and this process is repeated. Make sure that the dynamic balance is within an acceptable range.
  • the balance correction processing is performed on the rotating shaft 7 with the turbine wheel 5 coupled thereto.
  • the rotating shaft 7 in this state is installed on the balancing machine BM, and the machining positions P3 and P4 set at the front end corner and the back surface of the turbine wheel 5 are slightly measured while measuring the dynamic balance as in FIG. Reduce the dynamic balance to within the allowable range.
  • the balancing machine BM can measure the dynamic balance while rotating the rotating shaft 7 by blowing a predetermined inert gas Gas onto the turbine wheel 5.
  • the imbalance caused by such a bend is corrected by scraping the machining position P5 set on the head of the impeller nut 14 little by little while installing the balancing machine BM and measuring the dynamic balance.
  • the characteristic configuration of the bearing device 9 suppresses the occurrence of bending of the rotating shaft 7 on the turbine wheel 5 side when the impeller 12 is assembled, and the unbalance associated with the bending is concentrated on the impeller side 12. . For this reason, it is possible to keep the entire dynamic balance within the allowable range only by performing the correction process on the impeller 12 side without performing the correction process on the turbine wheel 5 side.
  • FIG. 3 is an enlarged view of the bearing device 9 shown in FIG. 1 and its periphery.
  • the bearing device 9 is disposed between the turbine wheel 5 and the impeller 12, more specifically, between the large-diameter turbine side step portion 20 formed on the rotary shaft 7 and the impeller 12.
  • the rotary shaft 7 is rotatably supported.
  • the bearing device 9 has a turbine-side ball bearing 21 in which balls 23 are positioned on the turbine wheel 5 side, an impeller-side ball bearing 22 in which balls 24 are positioned on the impeller 12 side, and these ball bearings 21 and 22 are held in the bearing housing 10. And a holder 25 for the purpose.
  • Each of the ball bearings 21 and 22 is configured as an angular contact type ball bearing.
  • the turbine-side ball bearing 21 has an outer ring 31 whose outer periphery is fitted in the holder 25, and an inner ring 32 that is coaxially disposed on the inner peripheral side of the outer ring 31 and is attached to the rotary shaft 7.
  • the inner ring 32 holds the ball 23 in a rollable state.
  • the impeller-side ball bearing 22 includes an outer ring 33 whose outer periphery is fitted in the holder 25 and an inner ring 34 that is coaxially disposed on the inner peripheral side of the outer ring 33 and is attached to the rotary shaft 7.
  • the inner ring 34 holds the ball 24 in a rollable state.
  • the inner ring 32 of the turbine-side ball bearing 21 extends in one direction from the holding position of the ball 23 toward the impeller 12 side, and an inward flange as a protruding portion protruding toward the center side of the rotating shaft 7 at the extended end.
  • a portion 37 is provided.
  • the inward flange portion 37 abuts a positioning step portion 38 formed on the rotating shaft 7.
  • the positioning step 38 is formed on the rotating shaft 7 so as to have a larger diameter toward the turbine wheel 5 side. Since the positioning step 38 restricts the movement of the inner ring 32 toward the turbine wheel 5, the turbine-side ball bearing 21 is positioned.
  • the position where the positioning step 38 is formed and the dimension of the inner ring 32 in the axis Ax direction are such that when the movement of the inner ring 32 is restricted by the positioning step 38, the end 32a on the turbine wheel 5 side is on the turbine side.
  • Each is set so as to be separated from the stepped portion 20.
  • a gap G is formed between the end portion 32a and the turbine side stepped portion 20 without any members.
  • the inner ring 34 of the impeller side ball bearing 22 abuts against the inner ring 32 of the turbine side ball bearing 21 positioned by the positioning step 38 when the collar 16 is pressed along with the assembly of the impeller 12.
  • the impeller side ball bearing 22 is positioned by restricting the movement of the inner ring 34 toward the turbine wheel 5 side.
  • the impeller side ball bearing 22 is positioned integrally with the turbine side ball bearing 21 using the positioning step 38.
  • the end 32a on the turbine wheel 5 side of the inner ring 32 of the turbine-side ball bearing 21 does not abut against the turbine-side step portion 20 when the impeller 12 is assembled, so that the rotating shaft 7 is not bent on the turbine wheel 5 side. . That is, the bending of the rotating shaft 7 that occurs when the impeller 12 is assembled concentrates on the impeller 12 side. For this reason, as shown in FIG. 2C, the ball bearings 21 and 22 are positioned in association with the assembly of the bearing device 9 only by balance correction processing for the processing position P5 set on the impeller 12 side. It is possible to correct the imbalance that occurs due to the bending of the rotating shaft 7 associated with.
  • FIG. 4 is an enlarged view of the bearing device and its periphery according to the second embodiment.
  • the bearing device 40 rotatably supports the rotating shaft 7 between the turbine side stepped portion 20 and the impeller 12.
  • the bearing device 40 includes a turbine side ball bearing 41 in which a ball 43 is positioned on the turbine wheel 5 side, and an impeller side ball bearing 42 in which a ball 44 is positioned on the impeller 12 side.
  • Each ball bearing 41 and 42 is a holder. 25.
  • Each ball bearing 41, 42 is configured as an angular contact type ball bearing.
  • the turbine-side ball bearing 41 has an outer ring 51 whose outer periphery is fitted into the holder 25, and an inner ring 52 that is coaxially disposed on the inner peripheral side of the outer ring 51 and is attached to the rotary shaft 7.
  • the inner ring 52 holds the ball 43 in a rollable state.
  • the impeller side ball bearing 42 has an outer ring 53 whose outer periphery is fitted into the holder 25 and an inner ring 54 that is coaxially disposed on the inner peripheral side of the outer ring 53.
  • the outer ring 53 and the inner ring 54 rotate the ball 44. Hold in a movable state.
  • the inner ring 52 of the turbine side ball bearing 41 extends in one direction from the holding position of the ball 43 toward the impeller 12 side.
  • a small-diameter portion 55 to which the inner ring 54 of the impeller side ball bearing 42 is mounted is formed on the impeller 12 side of the inner ring 52.
  • a stepped portion 56 is formed at the base of the small diameter portion 55.
  • An inward flange portion 57 is provided at the distal end portion of the small diameter portion 55 as a protruding portion that protrudes toward the center of the rotating shaft 7 and abuts against a positioning step portion 58 formed on the rotating shaft 7.
  • the positioning step portion 58 is formed on the rotary shaft 7 so as to have a larger diameter toward the turbine wheel 5 side, and the formation position thereof is closer to the impeller 12 side than the center position P of the ball 44 of the impeller side ball bearing 42.
  • the movement of the inner ring 52 toward the turbine wheel 5 is restricted by the positioning step 58.
  • the turbine side ball bearing 51 is positioned.
  • the position where the positioning step 58 is formed and the dimension of the inner ring 52 in the axis Ax direction are such that when the movement of the inner ring 52 is restricted by the positioning step 58, the end 52a on the turbine wheel 5 side is the turbine side step.
  • Each is set so as to be away from the unit 20.
  • a gap G is formed between the end portion 52a and the turbine-side step portion 20 without any members.
  • the inner ring 54 of the impeller side ball bearing 42 is mounted on the outer periphery of a small diameter portion 55 formed on the inner ring 52 of the turbine side ball bearing 41.
  • the inner ring 54 abuts against the spacer 59 abutted against the stepped portion 56 when the collar 16 is pressed when the impeller 12 is assembled. Thereby, the impeller side ball bearing 42 is positioned by restricting the movement of the inner ring 54 toward the turbine wheel 5 side.
  • the end 52a of the inner ring 52 of the turbine-side ball bearing 41 does not abut against the turbine-side step portion 20 when the impeller 12 is assembled, so that the same effect as that of the first embodiment can be obtained. it can. Furthermore, in the second embodiment, the position where the positioning step 58 is formed is set closer to the impeller 12 than the center position P of the ball 44 of the impeller side ball bearing 42. Accordingly, the bending of the rotating shaft 7 can be further concentrated on the impeller 12 side. Thereby, the balance correction process after the impeller 12 is assembled is facilitated.
  • FIG. 5 is an enlarged view of the bearing device and its periphery according to the third embodiment.
  • the bearing device 60 rotatably supports the rotating shaft 7 between the turbine side stepped portion 20 and the impeller 12.
  • the bearing device 60 includes a turbine side ball bearing 61 in which a ball 63 is located on the turbine wheel 5 side, and an impeller side ball bearing 62 in which a ball 64 is located on the impeller 12 side.
  • Each ball bearing 61, 62 is a holder. 25.
  • Each ball bearing 61, 62 is configured as an angular contact type ball bearing.
  • the turbine-side ball bearing 61 includes an outer ring 71 whose outer periphery is fitted into the holder 25, and an inner ring 72 that is coaxially disposed on the inner peripheral side of the outer ring 71 and is attached to the rotary shaft 7.
  • the inner ring 72 holds the ball 63 in a rollable state.
  • the impeller side ball bearing 62 includes an outer ring 73 whose outer periphery is fitted into the holder 25, and an inner ring 74 that is coaxially disposed on the inner peripheral side of the outer ring 73 and attached to the rotary shaft 7.
  • the inner ring 74 holds the ball 64 in a rollable state.
  • An inner ring 72 of the turbine-side ball bearing 61 extends in one direction from the holding position of the ball 63 toward the impeller 12 side, and an inward flange as a protruding portion protruding toward the center side of the rotating shaft 7 at the extended end.
  • a portion 77 is provided.
  • the inward flange portion 77 abuts a positioning step portion 78 formed on the rotating shaft 7.
  • the difference from the first embodiment is that the length of the inner ring 72 of the turbine side ball bearing 61 is shorter than that of the first embodiment, and the formation position of the positioning stepped portion 78 that abuts the inward flange portion 77 is different from that of the rotary shaft 7. It is set near the center.
  • the positioning step 78 is formed on the rotary shaft 7 so as to have a larger diameter toward the turbine wheel 5, and the inward flange portion 77 abuts against the positioning step 78 toward the turbine wheel 5.
  • the movement of the inner ring 72 is restricted.
  • the turbine side ball bearing 61 is positioned.
  • the position where the positioning step 78 is formed and the dimension of the inner ring 72 in the axis Ax direction are such that when the movement of the inner ring 72 is restricted by the positioning step 78, the end 72a on the turbine wheel 5 side is the turbine side step.
  • Each is set so as to be away from the unit 20.
  • the gap G is formed between the end portion 72a and the turbine side stepped portion 20 without any members interposed between them.
  • a spacer 79 having a width in the direction of the axis Ax is interposed between the inner ring 74 of the impeller side ball bearing 62 and the inner ring 72 of the turbine side ball bearing 61. Therefore, when the collar 16 is pressed against the inner ring 74 of the impeller side ball bearing 62 as the impeller 12 is assembled, the collar abuts against the spacer 79 and the movement of the inner ring 74 is restricted, and the impeller side ball bearing 62 is positioned. That is, the impeller side ball bearing 62 is positioned together with the turbine side ball bearing 61 using the positioning step 78 with the spacer 79 interposed between the inner rings 72 and 74.
  • the end 52a of the inner ring 52 of the turbine-side ball bearing 41 does not hit the turbine-side stepped portion 20 when the impeller 12 is assembled, so that the machining accuracy of the inner ring 52 and the turbine-side stepped portion 20 is improved. Regardless, it is possible to prevent the rotating shaft 7 from being bent on the turbine side. Thereby, it is not necessary to correct the unbalance of the rotating shaft 7 due to the bending on the turbine side. Further, according to the third embodiment, since the spacer 79 is interposed between the inner rings 72 and 74, the dimensional error in the axis Ax direction of the inner rings 72 and 74 can be absorbed by correcting the width of the spacer 79. . Thereby, since the processing accuracy of the inner rings 72 and 74 whose level is increased by sharing the positioning stepped portion 78 can be relaxed by using the spacer 79, the processing of the inner rings 72 and 74 is facilitated.
  • FIG. 6 is an enlarged view of the bearing device according to the fourth embodiment and the periphery thereof.
  • the bearing device 80 rotatably supports the rotating shaft 7 between the turbine side stepped portion 20 and the impeller 12.
  • the bearing device 80 includes a turbine side ball bearing 81 in which a ball 83 is located on the turbine wheel 5 side and an impeller side ball bearing 82 in which a ball 84 is located on the impeller 12 side.
  • Each ball bearing 81, 82 is a holder. 25.
  • Each of the ball bearings 81 and 82 is configured as an angular contact type ball bearing.
  • the turbine-side ball bearing 81 has an outer ring 91 whose outer periphery is fitted into the holder 25, and an inner ring 92 that is coaxially disposed on the inner peripheral side of the outer ring 91 and is attached to the rotary shaft 7.
  • the inner ring 92 holds the ball 83 in a rollable state.
  • the impeller side ball bearing 82 has an outer ring 93 whose outer periphery is fitted into the holder 25 and an inner ring 94 disposed coaxially on the inner peripheral side of the outer ring 93, and the outer ring 93 and the inner ring 94 rotate the ball 84. It is held in a movable state.
  • the inner ring 92 of the turbine side ball bearing 81 extends in one direction from the holding position of the ball 83 toward the impeller 12 side.
  • a small diameter portion 95 to which the inner ring 94 of the impeller side ball bearing 82 is mounted is formed in a range from the intermediate position of the inner ring 52 to the end portion on the impeller side.
  • a step portion 96 is formed at the root of the small diameter portion 95.
  • the small-diameter portion 95 is provided with an inward stepped portion 97 that protrudes toward the center of the rotating shaft 7 and that protrudes against a positioning stepped portion 98 formed on the rotating shaft 7.
  • the positioning stepped portion 98 is formed on the rotating shaft 7 so as to increase in diameter toward the turbine wheel 5 side.
  • the inward stepped portion 97 hits the positioning stepped portion 98, the movement of the inner ring 92 toward the turbine wheel 5 is restricted. Thereby, the turbine side ball bearing 81 is positioned.
  • the position where the positioning step 98 is formed and the dimensions of the inner ring 92 in the direction of the axis Ax are such that when the movement of the inner ring 92 is restricted by the positioning step 98, the end 92a on the turbine wheel 5 side is on the turbine side.
  • Each is set so as to be separated from the stepped portion 20.
  • a gap G is formed between the end portion 92a and the turbine-side step portion 20 without any members.
  • the inner ring 94 of the impeller side ball bearing 82 is mounted on the outer periphery of a small diameter portion 95 formed on the inner ring 92 of the turbine side ball bearing 81.
  • the inner ring 94 abuts against the spacer 99 abutted against the step portion 96 when the collar 16 is pressed when the impeller 12 is assembled. Thereby, the impeller side ball bearing 82 is positioned by restricting the movement of the inner ring 94 toward the turbine wheel 5 side.
  • the end portion 92a of the inner ring 92 of the turbine side ball bearing 81 does not abut against the turbine side step portion 20 when the impeller 12 is assembled, so that the machining accuracy of the inner ring 92 and the turbine side step portion 20 is improved. Regardless, it is possible to prevent the rotating shaft 7 from being bent on the turbine side. Thereby, it is not necessary to correct the unbalance of the rotating shaft 7 due to the bending on the turbine side.
  • each ball bearing is realized by a positioning step formed on the rotating shaft, but as a positioning unit for positioning each ball bearing, a regulating member such as a pin is used instead of the step. It is also possible to position each ball bearing by providing the rotary shaft and regulating the movement of the inner ring by the regulating member. In addition, a positioning part is formed by forming the outer peripheral surface of the rotating shaft on which the inner ring is mounted in a tapered shape so that the outer diameter gradually increases toward the turbine wheel, thereby restricting the movement of the inner ring. It is also possible to position each ball bearing.
  • the inner ring of the turbine-side ball bearing is extended to a position biased toward the impeller side, and the extension end of the inner ring is restricted by the positioning portion, whereby the rotation shaft associated with the positioning of the ball bearing.
  • the present invention is not limited to this form. That is, the present invention suffices if the end on the turbine wheel side of the inner ring is separated from the turbine side stepped portion, and the axial direction of the inner ring of the turbine side ball bearing is within the limit where the end is separated from the turbine side stepped portion.
  • the dimension and the position of the positioning portion can be set as appropriate. Further, it is not essential to position the turbine side ball bearing and the impeller side ball bearing integrally, and the present invention can be implemented in a form in which these are positioned by separate means.
  • a gap is formed between the end of the inner ring of the turbine-side ball bearing and the stepped portion on the turbine side, but no member, an inner ring, It is also possible to implement the present invention in such a manner that another member such as a member that is more easily elastically deformed than the constituent material of the rotating shaft is inserted into the gap to fill the gap. If such other members are inserted into the gap, the inner ring and the turbine side stepped portion are not in direct contact with each other, so that no bending occurs on the turbine wheel side as the turbine side ball bearing is positioned. Can achieve the purpose.
PCT/JP2009/056305 2009-03-27 2009-03-27 ターボチャージャの軸受装置 WO2010109653A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US13/259,242 US8602655B2 (en) 2009-03-27 2009-03-27 Bearing unit for turbocharger
EP09842267.8A EP2420660B1 (en) 2009-03-27 2009-03-27 Bearing unit for turbocharger
JP2011505773A JP5120494B2 (ja) 2009-03-27 2009-03-27 ターボチャージャの軸受装置
PCT/JP2009/056305 WO2010109653A1 (ja) 2009-03-27 2009-03-27 ターボチャージャの軸受装置
CN200980158373.9A CN102365440B (zh) 2009-03-27 2009-03-27 涡轮增压器的轴承装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/056305 WO2010109653A1 (ja) 2009-03-27 2009-03-27 ターボチャージャの軸受装置

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WO2010109653A1 true WO2010109653A1 (ja) 2010-09-30

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CN102365440A (zh) 2012-02-29
EP2420660B1 (en) 2015-03-04
JP5120494B2 (ja) 2013-01-16
EP2420660A4 (en) 2013-08-21
EP2420660A1 (en) 2012-02-22
JPWO2010109653A1 (ja) 2012-09-27
US8602655B2 (en) 2013-12-10
US20120039555A1 (en) 2012-02-16

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